Fluid pump drive



y 1952 w. w. PAGET 2,603,980:

FLUID PUMP DRIVE Original Filed July 25, 1942 aw m W a, Q

3 Sheets-Sheet l llll l IIIII ATTORNE Y.

y 1952 w. w. PAGET 2,603,980

FLUID PUMP DRIVE Original Filed July 25, 1942 5 Sheets-Sheet 2 a w e j/VVENTOR. 2027? Z12 Payei. I

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July 22, 1952 w. w. PAGET FLUID PUMP DRIVE Original Filed July 25, 1942 3 Sheets-Sheet 5 M272 2% Payei.

ATTORNEY.

Patented July 22, 1952 Joy Manufacturing Company, Pittsburgh, Pa., a corporation of Pennsylvania Original application July 25, 1942, Serial No.

11, 1949, Serial No. 80,844

Divided and this application March 8 Claims. (Cl. 74364) This invention relates to a fluid pump and drive therefor and is a. division of Serial No. 452,299, filed July 25, 1942, now Patent 2,477,002, issued July 26, 1949.

The objects of this. invention are included among the objects set forth in the above identified parent case, but may be summarized herein as theprovision of afluid pump-and means for driving the same wherebyan adequate speed of the fluid pump may" be automatically obtained at all times, and whereby suitable manual controls may be superimposed; on the automatic controls. I i .;This and other objects are accomplished in a two-speed drive in which, with the power source rotating at a low speed,- drive through the power transmission is accomplished at thehigher speed ratio through a speed multiplication gear train, and whereby. at thehigher. speed of the drive motor .the drive is directv and therefore at a lower ratio.

In the drawings: H a

Fig. 1 is a longitudinal vertical sectional view substantially identical with Fig. 4 of the above identified parent application. x

. Fig. 2 is a view in section substantially on line 22 of Fig. 1.

Fig. 3 is an enlarged detail of a portion of Fig. 1, showing the clutch and associated mechanism on a larger scale.

. Fig. 4 is an enlarged transverse fragmentary sectional view showing a detail of the drive mechanism.

Fig. 5 is a view in section on line 5 5 of Fig. 4. Fig. 6 is a view in section'on line 6-5 of Fig. 4. Fig. '7 is an enlarged detail sectional view on the axis of the speed responsive device for conthe control mechanism at the right-hand end Fig. 11' is a view in section substantially on line lll l of'Fig. 10. .4, l, V V

Fig. 12 is a transverse vertical'sectional view Fig. fragmentary .e'nlarged' :hori zontal sectional view on line 13-43 of Fig. 1, showing .a detail of the hydraulic system.

Where possible, the reference numerals used in this application correspond exactly to the reference numerals used in the parent case. in order to make cross-reference to that case easier.

In the preferred embodimentof the invention shown, the pumping apparatus; generally designated 0., comprises amaincasing part 31 and a pair of coacting rotors32 and-33'. The rotor 32 is a male rotor. and comprises four helically arranged lobes 34. The female rotor 33 is'provided,.in the form shown, with six helically arranged.- grooves 31 each adapted to cooperate with the lobes of the rotor,32.

Each of the rotors 32,33 is herein shown supported at its. ends by stub shafts, the rotor 32 having a stub shaft 401at1itslow pressure end and a stub shaft 4| at its high pressure end; While the rotor 33 has a stub shaft 42 at its low pressure end and a stub'shaft'43 at its high pressure end. The stub shafts 40', 4], 42 and 43 are supported in suitable bearings 44, 5|, 45 and 52 respectively, which position the rotors so that no contact can take place between them and the ends of the casing. I

For the purpose of maintaining the rotors out of contact with each other they are connected by intermeshing helical gearslil) and Bi, the gear being splined, as at 62, to the stub shaft 4|, and the gear 6|;being splined, as at 6 3, to the stub shaft 43. The gears 60 and El areso'formed that their helix angles correspond in hand and lead to the helix angles of the rotors to which they are respectively fixed.- I

A drive shaft 10 is arranged in alinement with the stub shaft 43 and has adriving connection therewith aswill be described in detail below. The drive shaft is journaledby meansof aball bearing 12 engaging a cylindrical portion 13 on the drive shaft. Its other end is rotatably supported as later described. Surrounding a cylindrical hub portion 19 of the gear BI is a bearing sleeve 80, and a cylindrical portion 8| at the right hand end of the drive shaft I0 rotatably surrounds the bearing sleeve and is-journaled thereon. I g I Keyedto the periphery of the cylindrical portion 8| of the drive shaft is a member 82 having a number of recesses 83 formed therein receiving rollers 84 which are operative, as later. described, at times to effect a clutching between the member 82, and a cylindrically bored liner ring 86 keyed, as at 81, to the gear 6|. The recesses 83 have relatively straight fbasesu-rfac es pins 94' and'move 'the-plungers 92 against the rollers 84. The pins are supported in end closure or plate members 91 and 98, and the rollers have stems 99 loosely received in openings I in the means for initiating compressive action is described in detail in the above-identified parent application of which this is a division and will not be described here because it is not a part of this invention.

" As previously indicated, thepha'n'ge inspeed of operation of the compressor-and the loading and unloading are both hydraulically controlled, and

r I shall now describe the hydraulic system. There plates 91 and 98. These plates 9? and'98 are supported to turn with the member 82.

It will be evident, referring to Figs. 2 and 4, 7

that if the member 92 be driven counterclockwise it will, through the rollers 94, be connected to the liner ring 86 and through the latterdrive the gear BI and, by virtue of the connection of gear 6| to shaft 43, drive the rotor 33, while through the meshing of gear BI with gear 69 and the mounting of gear 60 on shaft M, rotor 32 will also be" driven. If the gear 6| be driven counterclockwise at a greater angularrate than themember- 82; it will not be connected to that {ember and may turn freely. in the direction mentioned, relative to it. 7

lt will be noted (Fig. 1) that the stub shaft M has'another shaft I 02 connected with it. by means of'a splinedconnector element Iil3which hasan axial bore Ill li- -The lefthand'end of shaft I92, as viewedin Fig-1, is journaled in a ball bearing I llli 'ahd carriesagear I I3! somewhat smallerthan the gear 69'. A gear-I08, somewhat larger than the gear BI, meshes withthe-g'ear I9'I andis journaled by a ball bearing II I] on-a cylindrical portion III of the drive-shaft I9. It also has a sleeve portion: I I2, internallysplined at I I3 and supported by a ball bearing II 4 on a further cylindrical portion I I5 of the drive shaft I9.

' Discs I I! connected to the sleeve portion I I2 are interleaved withother discs H8 connected by splines I I9 to the drive shaft-Iii, which has a flange I 20 adjacent the bearing II i' serving as an abutment forthe end one of the interleaved series of discs I", II 8 when these are pressed together to connect the gear IUBto the drive shaft ment for a flexed annular spring I28 whose opposite side presses upon the side of the plate I25, and the spring I28 normally maintains the follower'member I22 in clutch unloading position. --It may now be noted that when the clutch is loaded, the gear I08 will be connected directly to the shaft I0 and will drive the gear I91 and so the gears 60 and GI, and thus the rotors 32 and 39;and because the gear BI will then be rotated faster than the member 82, and in the same direction with the latter, there will simply bean overrunning clutch action and no'tendency for co'nnection'between gear'GI and member 82.

The compressor has automatic meansfor effecting change in'the manner (and accordingly in the speed) of drive thereof governed by a speed responsive device and it has automatic means for effecting the initiation of compressive action thereby, governed'by the pressure of the surrounding air. Both of these automaticv means are hydraulically operated; the hydraulic clutch operating means for -the"con1pres sor' drive has been described "above. The hydraulically'controlled is provided in the base of the casing 3| the sump IEO. This sump isdisposed between the lower wall of the rotor housing and an outer wall I6I forming anintegral part of the casing 3i. The chamber is, in the horizontal position of the compressonsubstantially horizontal, and a pump of the intermeshing gear type is positioned at the right-hand end of the casing as the same is viewed in Fig. 1, so that it is partially submerged and so that its intake isalways submerged (in the horizontal position of the casing) in the oil in the sump. 1

This pump, designated I62, may be any suitable liquid pump. Reference may be had to the parent application for the details of a satisfactory pump. but this. invention is not limited to suc'ha pump. An intake passage in the under side I61: conducts oil into the pump. The pumpdischarge communicates with passages I18 in the cover I10, and H9 in'a supplemental cover, and opens into thebore Ififlofasleeve member I13. From this latter the fluidiis discharged'through branchpassageslal .(Fig. 13) :into a chamber I82 containing a strainer structure I93. Between the ends of the chamber I82 and suitablyassocia'ted with the strainer is an annular peripheral member having a peripheral 'i groove I86 to which. the strained lubricant obtains access through radial ports I85. The annular groove I84 communicates with a passage I86 which opens'into anannular groove I81 surrounding the bearing bushing 45; The opposite side of the annular groove I81 opens into a passage I88 whose upper end opens'into a chamber I89. Thechamber I89; constitutes a distribution point for oil for lubricating purposes and for operating the speed-changing clutch mechanism previously describedand' also for fluid to operate the air pressure controls. describedin detail in the parent case. I

*In line withthe passagefllflil there. isxanother passage I99 opening outwardandupwardfrom the. chamber I89. This communicates with an annular groove I92 in the. bushing 44'. The annular groove has continuously in communication with itv obliquely disposed passages I93 opening into'a chamber I94 in the stub shaft 40. The chamber I 94, tube I95-,.and associated mechanism have to. do withsubject: matter disclosed' and claimed in the parent application, andwillnot be reviewed here. It will be notedthatin the stub shaft 40* there is, at the right hand end of; the; chamber I94, a partition 2H! to the right of whichthere is a valve-receiving bore;2 I I. Otherobliquely extending passages 2I2 connectthe annular groove I92 with the bore 2I I at points near the :partition 2 I0, and a further annular passage 2I3 formed in the bushing is connected With the interior ofthe bore 2I I by radial passages 2M.

suitably supported on the'rear, end ofthe stub shaft 40 is a support or mounting2 I Sfor a speedresponsivegovernor 2I6 which servesinconiunction with a spring 2I.I housed. in-fthev interior-of a valve member 2 I8, to .varytheposition of that valve member in the be '2] I Thevalve-member will be observed to 'befop'e'n from end to eiia, as

at 228, and to house the spring 2.11 withinit in such a manner that thespring acts on the righthand end of the valve in Fig. 7 at one end and at its other end. acts on the partition or wall 2 I 11.

The valve has a left-hand end collar 222, another annular peripheral collar 223 spaced by a groove 224 from the collar 222 and a further enlarged collar--right-hand portion 225-spaced by aperipheral groove226 of substantial length from the collar portion 223. The support member 215 has a portion 221 guidingly engaging the head 225 and is traversed by openings 228 so that in certain positions of the valve 218 there may be a discharge into a chamber 230 at the right hand end of the compressor, of :fluid entering the chamber 211 through the radial passages 214.

The governor support 215'includes fly weights 232 pivotally supported on transverse pins 233 in earlike portions 234 carried by the support 215. Portions 235 of the fly weights at the opposite side of the pivots thereof from the main masses of said fly weights carry adjustable screw devices 236'which have heads 231 adapted to engage the end surface of the head 225, and upon the attainment of the shaft 40 to a predetermined speed of rotation the fly weights actuate the portions 235 to move the valve 218 to shift the valve from the position shown in Fig. 7 to that shown in Fig. 8, thereby allowin fluid entering the bore 211 through the radial passages 214 to be vented while at the same time preventing any delivery of fluid from the pump to the radial passages 214.

Cutting off the supply of fluid to the radial passages 214, and venting fluid from these passages through the bore 211. will effect, as shortly described, a reduction in the speed of the rotors. This reduction in speed, however, will not be sufficient to effect an operation of the speed governor permitting the valve to move again to a position for supplying fluid to the passages 214, as the design of the governor is such that it becomes operative to force the valve 218 to the left only. upon the attainment of a speed as of the order of I000 R. P. M., while after once assumin 'the position of Fig. 8 a reduction of the speed to a lower speed of the order of 4000 R. P. M. will be necessary before the weights will be moved in and permit the reestablishment of fluid delivery to the chamber 126 of the hydraulically operated clutch mechanism.

The circumferential groove 213 is connected below the stub shaft 40 with a passage 241 which extends downward parallel to the axis of the passage-190 and opens through an opening 242 into the interior of the bore of a valve-receiving bushing or sleeve 243. This valve-receiving bushing contains a rotatable valve 244, which is used primarily for testing purposes and which has an operating handle 245 by means of which the valve may be turned into any one of three different positions. v

In the position of the valve 244 shown in Fig. 1, a diametric passage 246 connects the opening 242 with an opposite opening 241 in the valve sleeve and via the latter opening to the passage 248 which is connected through a port 249 in a bearing sleeve 41 and an annular groove 250 and radial passages 251 with a chamber 252 within the interior of the stub shaft 42. The outer end of this chamber 252 is closed by a plug 253, while the other end of the chamber 252 is connected by a suitably centered tube 255 with arrangements for effecting the operation of the clutch mechanism previously described and for the performance of certain lubricating functions.

' Before proceeding with the description of this mechanism, it may be pointed out that below a predetermined speed of rotor 32, valve 218 will be in the position shown in Figs. 1 and '1 and will connect the pump discharge through the ports and passages previously described with the tube 255, but that, above such a predetermined speed, the valve 218 will assume the position shown in Fig. 8 and cut off communication completely between the passages and 241 and vent 241 back to the sump through the chamber 230.

Now it will be, observed, referring particularly to Figs. 1 and 3, that at the rear end. of the tube 255 there is a hell or funnel shaped member 251 fitting the bore 258 ofthe stub shaft 43, and that a split spring ring 259 operates to prevent possible movement of the member 251 out of the bore in the stub shaft if any loosening should occur. Within a stepped bore 260 within the drive shaft 10 there is arranged a hollow plunger member 261 which is provided at one end with a perforated flange 262 adapted to seat against a split ring 263 secured within the inner wall of the drive shaft 18. The plunger member 261 is engaged by a spring 264 which reacts against a shoulder 265 within the drive shaft, and a thimble 266 closes the lefthand end of the chamber within which the element 261 is movable. The interior of the chamber communicates, through obliquely radially extending passages 261, with the outside of the drive shaft between the ball bearings 12 and 1 18. Other radially obliquely extending passages 268 connect the interior. of the stepped bore 260 at the right hand end of the plunger member 261 in communication with the chamber 126.

The mode of operation of the mechanism which has just been described is as follows: When the compressor is started, a driving connection is immediately established between the shaft 111 and the gear 61 and the pump 162 commences to deliver fluid through the strainer, through the passage 186, the chamber 189, the passage 190, the oblique passages 212, the annular groove 224, the radial passages 214, passages 241, 246, 248, 251 and the tubular conduit 255 to the interior of the member 251 and to the space between that member and the plunger member 261. The fluid immediately passes through the perforations in the v flange 262 and through the radial passages 268 into the chamber 126 and brings the clutch discs 1 11 and 118 into contact with each other.

As the oil continues through the tube 255, the member 261 moves to the left, in effect increasing the volume of the conduit and compressing the spring 264; the compression of this spring is so determined that the clutch pressure will be gradually applied as the-member 261 moves to the left. Just before member 261 reaches its extreme left-hand position, the resistance of spring 264 is such that the pressure in'the hydraulic system is just below the value at which the relief valve opens. When member 261 reaches its extreme left-hand position, it can yield no further, whereupon the pressure in the hydraulic system immediately builds up to the value determined by the relief valve. The clutch discs are by then firmly pressed together and drive of the rotors at the higher speed by gear 108 will be effected. It will be appreciated that this high speed driving will be continued until the speed of the compressor builds up to such a degree that the valve 218 will be shifted by the governor, and then the slower speed drive between the shaft '10 and the compressor will be initiated. It will be noted that lubricant will be suppliedfrom the 7 space betweerr the member 2 6 Land the memher 25 !"tothe splines. f 7 V "'I he'man'ually operable valve. 2 previously." mentioned can beadjusted as: previously described to ;such a position as to .restore high speed drive of the compressor after such high speed drive has-been automatically interrupted, or to prevent interruption of high speed drive upon theattainment of the predetermined speed of operation at which a-shiftto low speed drive is normally effected-l Furthermore, in another position of. adjustment, this valve may be so operated as to preclude the high speed. drive completely.

Itwill be noted that in addition to the. diametric passage 241; formed in. the. valveithere is'a longitudinal peripheral passagei 210 which opensinto' the space'zll at: the right hand side of the valve, aspace which is. connected by a passage 211 (Fig; lJ'with the chamber 230'which communicates with the sump. When the valve 244 .is turned to bring the passage. 210' into com munication with the passage 2 l8'and to-bl'ank off the port 242 with the cylindrical portion of the valve' opposite the groove 21.0, it will be evidently impossible to transmit pressure. through thetube 255 for effecting high speed: drive of the compressor."

The valve ZMalso has an oppositely extending longitudinal peripheral' groove 2.14 opening through its end which forms a. portion of. the bounding wall of the chamber 189. When the valve is turned so as to bringi groove 214 into communication withthe passage 248; fluid will be supplied from the chamber- I 89 continuously to. the passage 2138'v and the tube 255'. and. high speed drive of the compressorzwill'alone.be possible.. Fig; 1 shows. means for. locking the handle 26% of the valve 2 inmid position where. the drive of the compressor'is. controlledby its speed automatically by the speed governor; the means comprises a'recess in the end cover plate and a cooperatingscrew in the handle 2:45. Other similar recesses (not shown) are. provided for the other two. positions ofthe handle.

- The chamber I89: has a laterally extending passage 2'16. communicatingxwith the. same; Thispassage is. adapted: to be connected by a longitudinally extendingpassage 21'! under the control of a spring-loadedvalve. 218 with". a pas:- sage Happening into. an annular chamber. 280 which surrounds the sleeve 243 and whichis connected at its. opposite side with. a passage 28!. The functionof. the spring loaded valve 218 is to maintain asufiicient pressurein the chamber I89 under. all circumstances when the compressor is running; to insure the operation of the speed change mechanism.

The passage 281- hasabore 2B2 communicating with it, and a valve'283 reciprocates in the bore. A side vent 284: opens out of the bore and leads into the space 230, and a spring 285 having an adjustable follower 285' is adapted. to control the pressure in the passage 281.

An extended summary of'thezmode of. operation of. the illustrative'embodiment of the invention which has. now been described in detail is not necessary in View of the explanations given of the modes of operation of the component parts; It may be noted, however, that when the compressor is caused to rotate, it will be started initially at the slower speed, drive being from the drive shaft; through: the automatic roller clutch. mechanismi to. the gearfil'. As soon as the compressor. has 'np'erated'i long enough to produce. the necessary oil. pressure. inthe system..ai thing which "occursralmost instantly-the high speed drive: orthe. compressor. rotors will be initiated unlessthe manual control valve.244 should have been. moved to prevent. this-an unlikely condition as. this.;valve. is" used mainly for test. purposes.

Obviously; if a substantial; perio'dof. idling is desired prior to takeoff (assuming ior'illustra-e tion thatthe. inventions isfapplied to. aircraft), this valve could be somanipulated as tov prevent theneedless displacement of air by the compressor. As; soonas the compressor attains a certain. predetermined driving speed, the automatic. speed governor mechanism will shift the valve 2l8 to substitute the low' speed drive for the; high speed. drive by interrupting. the supply oi: clutch l'oading' pressure. to. the: friction clutch loading member. 122'. Thusduring the relatively high speed. operation of the: compressor during flightirthe. low speed drive will be in operation. The nature' of th'egovernor is such as to. avoid hunting, and: when the. speed of. the compressor is: brought upto a valuesufficient to initiate low speeddrivethere; will be required. a greater reduction in; speed than will be occasioned bythe change from. one drive to the other before the I compresson'will again-shift back to the high speed; drive:

A555 result or this" invention be'noted thata novelairpump?or'compressor is provided havingnovel control: mechanism. It will further be:evident that. by theprovision'of'the novel construction and-arrangement'of parts, an air pump or compressor is. provided which is extremely compact and relatively light; in; weight. Other uses and advantages of. theginventi'on will be obvious to those skillediintheart.

While there is, in thissapplication specifically described; one form. which: the invention may assumeinpractice, it will be: understood that this: form. is. shown forpurposes, of illustration andthatthe invention, may be modified and embodied in variousaother forms without departing from its spirit or the scope of the appended claims.

I claim: 1; Ina drive: mechanism having a driving shaft and'a driven shaft, one of'said shafts having a hollow end providing an external surface and an internal bore, a first. gear rotatably mounted. on said external surface, a second gear mounted on the other shaft; and keyed, thereto, drive means connectingsaid-first and second gears; an overrunning clutch; connecting. the hollow end. ofv said one shaft with the second gear;a hydraulicallyoperable clutch having elements connected to the hollow end of said one shaft and. toythe first gear, hydraulic means to engage theclutch, a source of hydraulic fluid under pressure, conduit means connecting; said source with said. hydraulic clutch-engaging means. the conduit means including said hollow end, ayieldable member in the hollow end portion of the conduit means and movable by hydraulic fluid pressure to increase the volume of theconduit means-, and means acting on the yieldable member in a direction to oppose movement thereof by thefiuid.

' 2-: Drive-mechanism asset forth in claim 1, in which the. last-named means. exerts a, steadily increasing orce as theyieldable member-is displaced. .3; In axdrive. mechanism having a driving shaft and a driven shaft; one of said shafts having a hollow end providing an external surface and an internal bore, a first gear rotatably mounted on said external surface, a second gear mounted on the other shaft and keyed thereto, drive means connecting said first and second gears, an overrunning clutch connecting the hollow end of said one shaft with the second gear, a hydraulically operable clutch having elements connected to the hollow end of said one shaft and to the first gear, hydraulic means to engage the clutch, a source of hydraulic fluid under pressure, conduit means to deliver fluid under pressure from the source to said hydraulic clutch-engaging means, the conduit means including said hollow end, a fluidmovable member in the hollow end portion of the conduit means and yieldable under fluid pressure to permit enlargement of the conduit means, and means to limit movement of said member when the fluid in the conduit means is at such a pressure as to effect maximum engagement of the hydraulically operable clutch.

4. Drive mechanism as set forth in claim 3, and means opposing movement of the fluid-movable member, the opposition force exerted thereby increasing with movement of the movable member.

5. In a drive mechanism having a driving shaft and a driven shaft, one of said shafts having .a hollow end providing an external surface and an internal bore, a first gear rotatably mounted on said external surface, a second gear mounted on the other shaft and keyed thereto, third and fourth gears meshing with said first and second gears respectively, a drive connection between the third and fourth gears, an overrunning clutch connecting the hollow end of said one shaft with the second gear, a hydraulically operable clutch having elements connected to the hollow end of said one shaft and to the first gear, hydraulic means to engage the clutch, a source of hydraulic fluid under pressure, conduit means connecting said source with said hydraulic clutch-engaging means, the conduit means including said hollow end, and a yieldable member in the hollow end portion of the conduit means and movable by hydraulic fluid pressure to increase the volume of the conduit means.

6. Drive mechanism as set forth in claim 5, and means opposing movement of the yieldable member, the opposition force exerted thereby increasing with movement of the yieldable member.

7. In a drive mechanism having a driving shaft and a driven shaft, said shafts being coaxially aligned and one of them having a hollow end providing an external surface and an internal bore, a first gear rotatably mounted on said external surface, a second gear mounted on the other shaft and keyed thereto, drive means connecting said first and second gears, an overrunning clutch connecting the hollow end of said one shaft with the second gear, a hydraulically operable clutch mounted on said hollow end and having elements connected to the hollow end and to the first gear, hydraulic means to engage the clutch, a source of hydraulic fluid under pressure, conduit means to connect said source with the hydraulic means to engage the clutch, the conduit means including said hollow end, and a yieldable member in the hollow end portion of the conduit means and reciprocable to increase the volume of the conduit means.

8. Drive mechanism according to claim '7, in

which the first-named gear is provided with a sleeve portion which is spaced from said external surface to provide an annular space between the sleeve portion and said surface, the hydraulically operable clutch being disposed in the annular space.

WIN W. PAGET.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS 

